JP5884725B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus that cools a plurality of objects to be cooled.

  Conventionally, in an electric vehicle such as an electric vehicle or a hybrid vehicle, electric power stored in a secondary battery is supplied to an electric motor via an inverter or the like to output a driving force for traveling the vehicle. Secondary batteries typified by lithium ions and the like generate Joule heat due to electric power being taken in and out during running and charging, and the temperature rises. However, when the temperature exceeds a predetermined temperature, the secondary battery is deteriorated or damaged. Therefore, a cooling means for maintaining the temperature below a predetermined temperature is required.

  Patent Document 1 discloses a cooling means that uses a vapor compression refrigeration cycle that cools indoor air blown into the passenger compartment. In the refrigeration cycle apparatus disclosed in Patent Document 1, a first evaporator that cools indoor air and a second evaporator that cools a secondary battery are arranged in parallel on the refrigerant flow downstream side of the radiator. It is.

JP 2003-279180 A

  However, when the secondary battery is cooled using the refrigeration cycle as in the refrigeration cycle apparatus described in Patent Document 1, there are the following problems.

  In general, components such as compressors and radiators that make up the refrigeration cycle are placed in the engine room or hood in the front part of the vehicle, whereas secondary batteries are used in the vehicle to secure mounting space. It is placed under the passenger's floor in the center or under the rear seat or luggage under the rear of the vehicle. For this reason, the refrigerant piping connected to the second evaporator, that is, the forward refrigerant piping from the branching portion on the downstream side of the refrigerant flow of the radiator to the second evaporator, and the upstream side of the refrigerant flow of the blower from the second evaporator The return refrigerant pipe to the section is longer than the refrigerant pipe connected to the first evaporator. The length of the refrigerant pipe connected to the second evaporator is about 5 m one way depending on the location of the second evaporator.

  In the refrigeration cycle apparatus described in Patent Document 1, when the secondary battery is cooled, the high-density liquid refrigerant that has flowed out of the radiator passes through the long outbound refrigerant pipe described above and is disposed in the vicinity of the second evaporator. After being depressurized by the reduced pressure reducer, it flows into the second evaporator.

  Here, as described above, since the outbound refrigerant pipe of the second evaporator is long, the internal volume of the outbound refrigerant pipe is large, and there are many high-density liquid refrigerants in the outbound refrigerant pipe. For this reason, in the refrigeration cycle apparatus described in Patent Document 1, the refrigerant filling amount of the entire refrigeration cycle is significantly increased as compared with the refrigeration cycle apparatus having only the first evaporator. In addition, for example, the difference in the amount of refrigerant required for each operation mode becomes large, for example, when cooling alone with the first evaporator or when cooling alone with the second evaporator. An increase in the amount of refrigerant enclosed leads to an increase in refrigerant cost, and a large difference in the amount of necessary refrigerant leads to an increase in the volume of equipment that stores excess refrigerant in the cycle.

  In addition, although the case where the indoor blowing air was cooled by the first evaporator and the secondary battery was cooled by the second evaporator was described here, the present invention is not limited to this case, and the first evaporator uses the first evaporator. Such a problem also occurs when the object to be cooled is cooled and the second object to be cooled is cooled by the second evaporator.

  In view of the above points, an object of the present invention is to provide a refrigeration cycle apparatus capable of reducing the amount of refrigerant enclosed in the entire refrigeration cycle and reducing the difference in necessary refrigerant amount for each operation mode.

In order to achieve the above object, in the invention described in claim 1,
A compressor (11) for compressing and discharging the refrigerant;
A radiator (12) that dissipates the refrigerant discharged from the compressor;
First and second pressure reducers (16, 19) arranged in parallel on the downstream side of the refrigerant flow of the radiator and depressurizing the refrigerant flowing out of the radiator;
A first evaporator (17) for cooling the first cooling object and evaporating the refrigerant by heat exchange between the refrigerant depressurized by the first pressure reducer and the first cooling object;
A second evaporator (18, 71, 81) for cooling the second cooling object and evaporating the refrigerant by heat exchange between the refrigerant decompressed by the second decompressor and the second cooling object;
A refrigerant flow path branched from a branch portion (20) provided on the downstream side of the refrigerant flow of the radiator, and first and second forward paths (leading from the branch portion to the refrigerant inlets of the first and second evaporators) 22, 23)
A refrigerant flow path that merges with a merging section (24) provided on the upstream side of the refrigerant flow of the compressor, the first and second return paths (leading from the refrigerant outlet of the first and second evaporators) to the merging section ( 25, 26)
The second forward path (23) has a longer refrigerant flow path length than the first forward path (22),
The second pressure reducer (19) is disposed closer to the branching portion than the second evaporator in the second forward path,
Of the second forward path, the portion (23b) on the downstream side of the refrigerant flow with respect to the second pressure reducer is a double pipe (28) having an inner pipe (28a, 28c) and an outer pipe (28b, 28d) covering it. Consists of an inner pipe,
At least a part of the second return path (26) is constituted by an outer pipe.

  The “heat exchange between the refrigerant and the first object to be cooled” and the “heat exchange between the refrigerant and the second object to be cooled” are not limited to direct heat exchange but indirectly through a heat medium. This also includes the case of heat exchange.

  According to the present invention, since the second pressure reducer is arranged on the branch portion side of the second forward path, compared to the case where the second pressure reducer is arranged on the second evaporator side of the second forward path, The section in which the high-density liquid refrigerant flows in the second forward path is shortened, and the section in which the low-density gas-liquid two-phase refrigerant is decompressed after being depressurized by the second decompressor is lengthened, thereby reducing the amount of refrigerant existing in the second forward path. it can. Therefore, according to the present invention, it is possible to reduce the refrigerant filling amount of the entire refrigeration cycle and the difference in the necessary refrigerant amount for each operation mode.

  Furthermore, according to the present invention, the section in which the second-phase gas-liquid two-phase refrigerant flows is constituted by the inner pipe of the double pipe, and the second return path is constituted by the outer pipe of the double pipe. As compared with the case where the second forward path is configured by a single pipe, the refrigerant flowing through the refrigerant can suppress heat reception from the outside of the gas-liquid two-phase refrigerant flowing through the second forward path. As a result, according to the present invention, the cooling performance of the second evaporator can be improved as compared with the case where the second forward path is configured by a single pipe.

  In the second aspect of the present invention, the refrigerant pressure at the refrigerant outlet of the second evaporator is the refrigerant pressure at the refrigerant outlet of the first evaporator in the operation mode in which the refrigerant flows through both the first and second evaporators. The channel cross-sectional area (S2) of the outer tube is smaller than the channel cross-sectional area (S1) of the inner tube in at least a part of the double tube.

  According to this, in the operation mode in which the refrigerant flows in both the first and second evaporators, the pressure loss in the second return path becomes larger, so that the refrigerant on the second evaporator side than the refrigerant pressure on the first evaporator side. High pressure can be maintained. If the refrigerant temperature of the second evaporator is desired to be higher than the refrigerant temperature of the first evaporator, this can be achieved by adding a decompressor such as a fixed throttle to the second return path. This is possible without adding a decompressor to the second return path.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole block diagram which shows the refrigerant | coolant flow in the air_conditioning | cooling independent operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the battery cooling single operation mode of the refrigeration cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the battery cooling + air_conditionaing | cooling operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a cross-sectional view of the double pipe in FIGS. It is a Mollier diagram which shows the state of the refrigerant | coolant in the air_conditioning | cooling independent operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant in the battery cooling single operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant in the battery cooling + air_conditioning | cooling operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is sectional drawing of the outward refrigerant | coolant piping and the backward refrigerant | coolant piping of the conventional battery cooling evaporator. It is sectional drawing of the outward refrigerant | coolant piping and the return refrigerant | coolant piping of the evaporator for battery cooling in a comparative example. It is a whole block diagram which shows the refrigerating-cycle apparatus of 2nd Embodiment. It is a whole lineblock diagram showing the refrigerating cycle device of a 3rd embodiment. It is a perspective sectional view showing the structure of the double tube of a 4th embodiment. It is a figure which shows the cooling mechanism of the secondary battery of 5th Embodiment. It is a figure which shows the cooling mechanism of the secondary battery of 6th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be described with the same reference numerals.

(First embodiment)
In the present embodiment, the refrigeration cycle apparatus 10 according to the present invention is applied to a hybrid vehicle that obtains driving force for traveling from a traveling electric motor and an internal combustion engine. Furthermore, in the hybrid vehicle of the present embodiment, as shown in FIGS. 1 to 3, the refrigerating cycle device 10 cools the secondary battery 53 that stores power supplied to the cooling of the passenger compartment and the electric motor for traveling. It is used to do.

  The refrigeration cycle apparatus 10 has a configuration in which a secondary battery cooling function is added to the basic cycle with the receiver cycle for air conditioning as the basic cycle. This basic cycle includes various devices such as a compressor 11, an outdoor condenser 12, a cooling expansion valve 16, an indoor evaporator 17, and the like. Each of these devices is connected by a refrigerant pipe. In this basic cycle, a battery cooling evaporator 18 is disposed in parallel with the indoor evaporator 17 on the downstream side of the refrigerant flow of the outdoor condenser 12, and the battery cooling evaporator 18 is disposed on the upstream side of the refrigerant flow of the battery cooling evaporator 18. An expansion valve 19 is arranged.

  Regarding the correspondence between this embodiment and the claims, the outdoor condenser 12 corresponds to a radiator, the cooling expansion valve 16 corresponds to a first pressure reducer, and the indoor evaporator 17 corresponds to a first evaporator. Correspondingly, the battery cooling expansion valve 19 corresponds to the second decompressor, and the battery cooling evaporator 18 corresponds to the second evaporator. Moreover, the indoor air blown into the passenger compartment is the first object to be cooled, and the secondary battery 53 is the second object to be cooled.

  The refrigeration cycle apparatus 10 employs an HFC refrigerant or the like as the refrigerant, and constitutes a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.

  Hereinafter, the refrigeration cycle apparatus 10 will be described in detail.

  The compressor 11 sucks the refrigerant in the refrigeration cycle apparatus 10 and compresses and discharges the refrigerant. The compressor 11 is configured as an electric compressor that rotationally drives a fixed capacity type compression mechanism with a fixed discharge capacity by an electric motor. The rotation speed of the electric motor of the compressor 11 is controlled by a control signal output from the control device 40 described later. The refrigerant inlet side of the outdoor condenser 12 is connected to the discharge port side of the compressor 11.

  The outdoor condenser 12 functions as a radiator that dissipates and condenses the refrigerant discharged from the compressor by exchanging heat between the refrigerant flowing through the inside and the outside air blown from the blower fan 12a. More specifically, the outdoor condenser 12 is a so-called subcool condenser, and a condenser 13 that heat-exchanges the gas-phase refrigerant discharged from the compressor 11 and air to condense the refrigerant, and flows out of the condenser 13. The gas-liquid separator 14 that separates the gas-liquid of the refrigerant and the supercooling unit 15 that cools the liquid refrigerant flowing out of the gas-liquid separator 14 are provided.

  The refrigeration cycle apparatus 10 includes a refrigerant flow path 21 that guides the refrigerant flowing out of the outdoor condenser 12 to the branching section 20 and a refrigerant flow path branched from the branching section 20, and the refrigerant inlet of the indoor evaporator 17 from the branching section 20. And a second forward path 23 for guiding the refrigerant from the branch portion 20 to the refrigerant inlet of the battery cooling evaporator 18.

  The refrigeration cycle apparatus 10 is a refrigerant flow path that merges with the merge section 24, and includes a first return path 25 that guides the refrigerant flowing out from the refrigerant outlet of the indoor evaporator 17 to the merge section 24, and the battery cooling evaporator 18. A second return path 26 that guides the refrigerant flowing out from the refrigerant outlet to the junction 24 and a refrigerant flow path 27 that guides the refrigerant from the junction 24 to the suction side of the compressor 11 are provided.

  A first on-off valve 22 a and a cooling expansion valve 16 are provided in the first forward path 22.

  The first opening / closing valve 22 a is an electromagnetic valve whose opening / closing operation is controlled by a control voltage output from the control device 40. The presence or absence of the refrigerant flow in the first forward path 22 is switched by opening and closing the first on-off valve 22a. Therefore, the first on-off valve 22a constitutes a refrigerant flow path switching unit.

  The cooling expansion valve 16 is a pressure reducer that depressurizes the refrigerant that flows out of the outdoor condenser 12 and flows into the indoor evaporator 17. In this embodiment, as the cooling expansion valve 16, a mechanical expansion valve whose valve opening is adjusted so as to control the degree of superheat of the refrigerant flowing out of the indoor evaporator 17 to a predetermined value, for example, 5 ° C. is used.

  The indoor evaporator 17 is a heat exchanger that cools the indoor blowing air and evaporates the refrigerant by heat exchange between the refrigerant decompressed by the cooling expansion valve 16 and the indoor blowing air. The indoor evaporator 17 is disposed upstream of the air flow from the heater core 33 in the casing 31 of the indoor air conditioning unit 30.

  A second open / close valve 23 a and a battery cooling expansion valve 19 are provided in the second forward path 23.

  The second on-off valve 23a is an electromagnetic valve similar to the first on-off valve 22a. The presence or absence of the refrigerant flow in the second forward path 23 is switched by opening and closing the second on-off valve 23a. Therefore, the 2nd on-off valve 23a comprises the refrigerant | coolant flow path switching means.

  The battery cooling expansion valve 19 is a decompressor that decompresses the refrigerant flowing into the battery cooling evaporator 18. In this embodiment, as the battery cooling expansion valve 19, the degree of superheat of the refrigerant after flowing out of the battery cooling evaporator 18 and passing through the outer tube 28b of the double tube 28 described later is set to a predetermined value, for example, 5 ° C. A mechanical expansion valve whose valve opening is adjusted to be controlled is used.

  The battery cooling evaporator 18 is disposed in a battery pack 50 that forms an air passage for battery blowing air that is blown toward the secondary battery 53. The battery cooling evaporator 18 is a heat exchanger that cools the battery blowing air and evaporates the refrigerant by heat exchange between the refrigerant decompressed by the battery cooling expansion valve 19 and the battery blowing air. In other words, the battery cooling evaporator 18 is a heat exchanger that indirectly exchanges heat between the refrigerant and the secondary battery 53 via the battery blowing air.

  The compressor 11, the outdoor condenser 12, the battery cooling expansion valve 19, the branch portion 20, the first and second on-off valves 22 a and 23 a, and the merging portion 24 are disposed in the engine room E 1 at the front portion of the vehicle. . The cooling expansion valve 16 and the indoor evaporator 17 are disposed in the foremost part in the vehicle interior. The battery cooling evaporator 18 is disposed at the rear of the vehicle, and is further away from the engine room E1 than the indoor evaporator 17. For this reason, the refrigerant flow path length of the second forward path 23 is longer than that of the first forward path 22, and the refrigerant flow path length of the second return path 26 is also longer than that of the first return path 25.

  Further, the battery cooling expansion valve 19 is disposed in the vicinity of the branching portion 20, that is, disposed on the side closer to the branching portion 20 than the battery cooling evaporator 18 in the second forward path 23. Note that the battery cooling expansion valve 19 is not limited to the vicinity of the branching portion 20, and may be disposed closer to the branching portion 20 than the intermediate position of the second forward path 23.

  A portion 23b of the second forward path 23 on the downstream side of the refrigerant flow with respect to the battery cooling expansion valve 19 is composed of the inner pipe 28a of the double pipe 28 shown in FIG. 26a is composed of an outer tube 28b of the double tube 28 shown in FIG. The double pipe 28 has an inner pipe 28a and an outer pipe 28b covering the inner pipe 28a. Most of the double pipe 28 is disposed outside the passenger compartment under the vehicle floor and is covered with a cover or the like or exposed.

  In the present embodiment, as the double pipe 28, the inner pipe 28a is positioned inside the outer pipe 28b, and the outer diameter of the inner pipe 28a is smaller than the inner diameter of the outer pipe 28b. In this double tube 28, the refrigerant flow path of the outer tube 28b is formed between the outer surface of the inner tube 28a and the inner surface of the outer tube 28b, and extends in the same direction as the extending direction of the inner tube 28a.

  In the present embodiment, as will be described later, since the gas-liquid two-phase refrigerant flows through the inner tube 28a, the inner diameter of the inner tube 28a is set to 10.3 mm, which is the same as general gas refrigerant piping. Incidentally, since the liquid refrigerant flows in the forward piping of a general evaporator, its inner diameter is about 6 mm.

  Further, in the present embodiment, in the entire double pipe 28, the flow path cross-sectional area S2 of the outer pipe 28b is smaller than the flow path cross-sectional area S1 of the inner pipe 28a (S1> S2). ).

  Next, the indoor air conditioning unit 30 will be described. The indoor air conditioning unit 30 blows the temperature-adjusted indoor air to the vehicle interior, and is disposed inside the foremost instrument panel (instrument panel) in the vehicle interior and forms a casing 31 thereof. The blower 32, the above-described indoor evaporator 17, the heater core 33, and the like are accommodated therein.

  The casing 31 is made of resin, and forms an air passage for indoor blown air therein. On the most upstream side of the air flow in the casing 31, an inside / outside air switching device (not shown) that switches and introduces vehicle interior air (inside air) and outside air is arranged.

  The blower 32 blows air sucked through the inside / outside air switching device toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal multiblade fan with an electric motor, and the number of rotations (air flow rate) is controlled by a control voltage output from the control device 40.

  On the downstream side of the air flow of the blower 32, the indoor evaporator 17 and the heater core 33 are arranged in this order with respect to the flow of the indoor blown air. The heater core 33 is a heat exchanger for heating that heats indoor air by using cooling water of the internal combustion engine as a heat source.

  Further, on the downstream side of the air flow of the indoor evaporator 17 and on the upstream side of the air flow of the heater core 33, the air that adjusts the air volume ratio that passes through the heater core 33 among the blown air that has passed through the indoor evaporator 17. A mix door 34 is arranged. The air mix door 34 is driven by a control signal output from the control device 40.

  Further, a mixing space 35 is provided on the downstream side of the air flow of the heater core 33 to mix the blown air heated by exchanging heat with the refrigerant in the heater core 33 and the blown air that is not heated by bypassing the heater core 33. ing.

  A blow-off opening that blows the conditioned air mixed in the mixing space 35 into the vehicle interior, which is the air-conditioning target space, is disposed at the most downstream portion of the air flow of the casing 31. Specifically, the blowout opening includes a face blowout opening that blows conditioned air toward the upper body of an occupant in the vehicle interior, a foot blowout opening that blows conditioned air toward the feet of the occupant, and a vehicle front window glass. A defroster blowout opening (not shown) for blowing conditioned air toward the inner surface is provided.

  Therefore, the temperature of the conditioned air mixed in the mixing space 35 is adjusted by adjusting the ratio of the air volume that the air mix door 34 passes through the heater core 33, and the temperature of the conditioned air blown out from each outlet opening is adjusted. Adjusted.

  Further, on the upstream side of the air flow of the face blowing opening, the foot blowing opening, and the defroster blowing opening, the face door for adjusting the opening area of the face blowing opening and the opening area of the foot blowing opening are adjusted respectively. A defroster door (both not shown) for adjusting the opening area of the foot door and the defroster blowout opening is disposed.

  Next, the battery pack 50 will be described. The battery pack 50 is arranged on the vehicle bottom surface side between the trunk room and the rear seat at the rear of the vehicle, and is blown air for batteries in a metal casing 51 that has been subjected to electrical insulation processing (for example, insulation coating). An air passage for circulating and blowing air is formed, and the blower 52, the battery cooling evaporator 18, the secondary battery 53 and the like are accommodated in the air passage.

  The blower 52 is arranged on the upstream side of the air flow of the battery cooling evaporator 18, and blows the battery blown air toward the battery cooling evaporator 18, and the rotation speed is controlled by the control voltage output from the control device 40. This is an electric blower in which (the amount of blown air) is controlled. Further, a secondary battery 53 is arranged on the downstream side of the air flow of the battery cooling evaporator 18, and the downstream side of the secondary battery 53 communicates with the suction port side of the blower 52.

  Therefore, when the blower 52 is operated, the battery blowing air cooled by the battery cooling evaporator 18 is blown to the secondary battery 53, and the secondary battery 53 is cooled. Further, the blown air for the battery that has cooled the secondary battery 53 is sucked into the blower 52 and blown again toward the battery cooling evaporator 18.

  Next, the electric control unit of this embodiment will be described. The control device 40 is composed of a well-known microcomputer including a CPU, ROM, RAM and the like and its peripheral circuits, and performs various calculations and processing based on a control program stored in the ROM, and is connected to the output side. Controls the operation of various controlled devices.

  On the input side of the control device 40, an inside air sensor that detects the temperature inside the vehicle, an outside air sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and the temperature of the air blown from the indoor evaporator 17 (evaporator temperature) The first evaporator temperature sensor 41 for detecting the temperature, the heating air temperature sensor for detecting the air temperature of the heater core 33, the battery temperature sensor 42 for directly detecting the temperature of the secondary battery 53, and the air temperature of the battery cooling evaporator Various control sensor groups such as the second evaporator temperature sensor 43 to be detected are connected.

  Further, an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 40, and operation signals from various operation switches provided on the operation panel are input. As various operation switches provided on the operation panel, there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, an air conditioning operation mode selection switch, and the like.

  Note that the control device 40 of the present embodiment is configured such that control means for controlling various control target devices connected to the output side is integrally configured, but the configuration for controlling the operation of each control target device ( Hardware and software) constitute control means for controlling the operation of each control target device. For example, in the control device 40, the configuration (hardware and software) for controlling the operation of the compressor 11 constitutes the refrigerant discharge capacity control means, and the constitution for controlling the operation of various devices constituting the refrigerant flow path switching means. Refrigerant flow path switching control means is configured.

  Next, the operation of the refrigeration cycle apparatus 10 of the present embodiment having the above configuration will be described. As described above, the refrigeration cycle apparatus 10 can cool the passenger compartment and cool the secondary battery 53. The vehicle interior is heated by the heater core 33.

  Switching between the cooling mode for cooling the passenger compartment and the heating mode for heating the passenger compartment is performed by the control device 40 executing a control program stored in advance in the storage circuit.

  In this control program, the operation signal of the operation panel and the detection signal of the control sensor group are read, the control state of various control target devices is determined based on the read detection signal and the value of the operation signal, and the determined control state The control routine of outputting a control signal or a control voltage to various devices to be controlled is repeated.

  And about the operation mode at the time of air-conditioning of a vehicle interior, when the air conditioning operation switch is turned on (ON) and cooling is selected with the selection switch when the operation signal of the operation panel is read Is switched to the cooling mode, and when heating is selected by the selection switch while the air conditioning operation switch is turned on (ON), the mode is switched to the heating mode.

  As for the battery cooling operation mode for cooling the secondary battery 53, when the detection signal of the control sensor group is read, the battery temperature is higher than a predetermined temperature or the air temperature in the battery pack is higher than the predetermined temperature. Performed when high.

The operation in the main operation mode described above will be described below.
(A) Cooling single operation mode In the cooling single operation mode, the refrigerant flows only into the indoor evaporator 17 out of the indoor evaporator 17 and the battery cooling evaporator 18, so that the secondary battery 53 is not cooled, and the vehicle is cooled. This is an operation mode for cooling the room. This operation mode is executed, for example, when the operation switch on the operation panel is turned on (ON), cooling is selected by the selection switch, and the battery temperature is lower than a predetermined temperature.

  In this operation mode, the control device 40 opens the first on-off valve 22a and closes the second on-off valve 23a. Thereby, the refrigerating cycle apparatus 10 is switched to the refrigerant circuit through which a refrigerant flows as shown by the thick line and the solid line arrow of FIG.

  Moreover, the control apparatus 40 calculates the target blowing temperature TAO which is the target temperature of the air which blows off into a vehicle interior based on the value of the read detection signal and operation signal. Further, based on the calculated target blowing temperature TAO and the detection signal of the sensor group, the control device 40 operates the operation states of the various control target devices connected to the output side of the control device 40 (control to be output to the various control target devices). Signal).

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. Based on the target outlet temperature TAO, a target evaporator outlet temperature TEO of the indoor evaporator 17 is determined with reference to a control map stored in the control device 40 in advance. Based on the detection result of the evaporator temperature sensor 41, a control signal output to the electric motor of the compressor 11 is determined so that the temperature of the air blown from the indoor evaporator 17 approaches the target evaporator blowout temperature TEO. The In general, cooling requires a large cooling capacity of 1 to 5 kW, and the air temperature of the indoor evaporator 17 needs to be about 1 ° C. in order to ensure cooling performance and dehumidification performance. Therefore, in the present embodiment, the rotational speed of the compressor 11 is determined so that the temperature of the air blown from the indoor evaporator 17 is about 1 ° C.

  The control voltage output to the electric motor of the blower 32 of the air conditioning unit 30 is determined with reference to a control map stored in advance in the storage circuit, based on the target blowing temperature TAO. The control signal output to the drive unit of the air mix door 34 is determined so that the air mix door 34 closes the air passage of the heater core 33 and the entire amount of blown air after passing through the indoor evaporator 17 bypasses the heater core 33. Is done.

  Further, the blower 52 of the battery pack 50 is stopped. In addition, when cooling the secondary battery 53 only by ventilation, the air blower 52 may be operated.

  Then, a control signal or a control voltage is output from the control device 40 to the control target device so as to obtain the control state determined as described above.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling single operation mode, as shown in FIGS. 1 and 5, the refrigerant flows in the order of the compressor 11 → the outdoor condenser 12 → the cooling expansion valve 16 → the indoor evaporator 17 → the compressor 11. .

  At this time, in the indoor evaporator 17, the refrigerant decompressed by the cooling expansion valve 16 absorbs heat from the indoor air blown by the blower 32 and evaporates. Thereby, the air for room | chamber interior is cooled and air_conditioning | cooling of a vehicle interior is performed.

(B) Battery Cooling Single Operation Mode In the battery cooling single operation mode, the refrigerant flows only in the battery cooling evaporator 18 among the indoor evaporator 17 and the battery cooling evaporator 18, so that the vehicle interior is not air-conditioned. In this operation mode, the secondary battery 53 is cooled alone. This operation mode is executed, for example, when the operation switch of the operation panel is not turned on (OFF) and the battery temperature is higher than a predetermined temperature.

  In this operation mode, the control device 40 closes the first on-off valve 22a and opens the second on-off valve 23a. Thereby, the refrigeration cycle apparatus 10 is switched to the refrigerant circuit through which the refrigerant flows as shown by the thick line and the solid line arrow in FIG.

  With this refrigerant circuit configuration, the control device 40 determines the operating states of various control target devices connected to the output side of the control device 40 based on the detection signals of the sensor group.

  The refrigerant discharge capacity of the compressor 11 is controlled according to the required battery cooling capacity calculated based on the detected temperatures of the battery temperature sensor 42 and the second evaporator temperature sensor 43. The amount of heat generated by the battery during traveling is as small as several hundred watts, and is about 2 kW even during rapid charging at which maximum heat is generated. For this reason, the required battery cooling capacity is smaller than the cooling capacity. Therefore, in the present embodiment, the rotation of the compressor 11 is performed so that the temperature of the blown air from the battery cooling evaporator 18 detected by the second evaporator temperature sensor 43 is higher than the temperature of the blown air from the indoor evaporator 17. The number is determined.

  The control signal output to the blower 32 of the indoor air conditioning unit 30 does not require cooling, so the blower 32 is stopped. Note that the blower 32 may be operated when only blowing into the passenger compartment.

  About the control signal output to the air blower 52 of the battery pack 50, it determines so that the air blowing capability of the air blower 52 may become predetermined predetermined air blowing capability.

  Then, a control signal or a control voltage is output from the control device 40 to the control target device so as to obtain the control state determined as described above.

  Therefore, in the refrigeration cycle apparatus 10 in the battery cooling single operation mode, as shown in FIGS. 2 and 6, the compressor 11 → the outdoor condenser 12 → the branch portion 20 → the battery cooling expansion valve 19 → the inner pipe of the double pipe 28. The refrigerant flows in the order of 28a (refer to FIG. 4) → battery cooling evaporator 18 → double tube 28 outer tube 28b (refer to FIG. 4) → merging portion 24 → compressor 11.

At this time, the refrigerant that has flowed out of the outdoor condenser 12 is decompressed by the battery cooling expansion valve 19 to be in a gas-liquid two-phase refrigerant state, and after flowing through the inner pipe 28a of the double pipe 28 in that state, the battery cooling is performed. Flow into the evaporator 18. The refrigerant that has flowed into the battery cooling evaporator 18 absorbs heat from the battery air blown by the blower 52 and evaporates. As a result, the battery air is cooled and the secondary battery 53 is cooled.
(C) Battery cooling + cooling operation mode In the battery cooling + cooling operation mode, the refrigerant flows through both the indoor evaporator 17 and the battery cooling evaporator 18 to cool the secondary battery 53 and at the same time in the vehicle interior. This is an operation mode for cooling.

  In this operation mode, the control device 40 opens both the first on-off valve 22a and the second on-off valve 23a. Thereby, the refrigerating cycle apparatus 10 is switched to the refrigerant circuit through which a refrigerant flows as shown by the thick line and the solid line arrow of FIG.

  With this refrigerant circuit configuration, the control device 40 determines the operating states of various control target devices connected to the output side of the control device 40 based on the detection signals of the sensor group.

  About the refrigerant | coolant discharge capability of the compressor 11, based on the detection result of the evaporator temperature sensor 41 similarly to the cooling independent operation mode, the blowing air temperature from the indoor evaporator 17 approaches the target evaporator blowing temperature TEO. The control signal output to the electric motor of the compressor 11 is determined.

  About the control signal output to the air blower 32 of the air conditioning unit 30, and the air mix door 34, it determines similarly to the air_conditioning | cooling independent operation mode. The control signal output to the blower 52 of the battery pack 50 is determined in the same manner as in the battery cooling single operation mode.

  Then, a control signal or a control voltage is output from the control device 40 to the control target device so as to obtain the control state determined as described above.

  Therefore, in the refrigeration cycle apparatus 10 in the battery cooling + cooling operation mode, as shown in FIGS. 3 and 7, the compressor 11 → the outdoor condenser 12 → the branching section 20 → the cooling expansion valve 16 → the indoor evaporator 17 → the merging section The refrigerant flows in the order of 24 → the compressor 11, and the refrigerant flows in the order of the branch portion 20 → the battery cooling expansion valve 19 → the battery cooling evaporator 18 → the merging portion 24. In addition, in the Mollier diagram of FIG. 7, the refrigerant | coolant state when a refrigerant | coolant flows through the indoor evaporator 17 and the refrigerant | coolant flows through the battery cooling evaporator 18 is shown collectively for convenience.

  At this time, in the indoor evaporator 17, similarly to the cooling single operation mode, the refrigerant decompressed by the cooling expansion valve 16 absorbs heat from the indoor blown air blown by the blower 32 and evaporates. Thereby, the air for room | chamber interior is cooled and air_conditioning | cooling of a vehicle interior is performed.

  On the other hand, on the battery cooling evaporator 18 side, the refrigerant flowing out of the outdoor condenser 12 is decompressed by the battery cooling expansion valve 19 to become a gas-liquid two-phase refrigerant state, and in this state, the inner pipe of the double pipe 28 After flowing through 28a, it flows into the battery cooling evaporator 18. The refrigerant that has flowed into the battery cooling evaporator 18 absorbs heat from the battery air blown by the blower 52 and evaporates. As a result, the battery air is cooled and the secondary battery 53 is cooled.

  Here, in the present embodiment, as shown in FIG. 4, the entire double pipe 28 is configured such that the flow path cross-sectional area S2 of the outer pipe 28b is smaller than the flow path cross-sectional area S1 of the inner pipe 28a. This increases the pressure loss when the refrigerant flows inside the outer pipe 28b forming the second return path 26. In this case, the refrigerant pressure at the refrigerant outlet 18b of the battery cooling evaporator 18 increases compared to the case where the flow path cross-sectional area S2 of the outer pipe 28b is equal to or greater than the flow path cross-sectional area S1 of the inner pipe 28a. Since the refrigerant temperature also rises, the blown air temperature of the battery cooling evaporator 18 becomes high. In the present embodiment, by utilizing this, the refrigerant pressure of the battery cooling evaporator 18 is maintained higher than the refrigerant pressure of the indoor evaporator 17, and the temperature of the air blown from the battery cooling evaporator 18 is changed to the indoor evaporator 17. It is made to become higher than the blowing air temperature.

  Further, as a method of increasing the pressure loss of the refrigerant flowing through the second return path 26, there is a method of adding a decompressor such as a fixed throttle to the second return path 26, but according to the present embodiment, no additional decompressor is required. It becomes.

  In the present embodiment, the entire double pipe 28 is configured such that the cross-sectional area S2 of the outer pipe 28b is smaller than the cross-sectional area S1 of the inner pipe 28a. Instead, a part of the configuration may be used.

  Next, the effect of this embodiment will be described.

  In the present embodiment, the battery cooling expansion valve 19 is disposed in the second forward path 23 on the side closer to the branch portion 20 than the battery cooling evaporator 18.

  For this reason, according to this embodiment, compared with the case where the battery cooling expansion valve 19 is disposed in the vicinity of the battery cooling evaporator 18, there is a section where the high-density liquid refrigerant flows in the second forward path 23. Since the section where the low-density gas-liquid two-phase refrigerant after decompression flows through the expansion valve 19 for battery cooling flows becomes longer, the amount of refrigerant existing in the second forward path 23 can be reduced.

More specifically, unlike the present embodiment, when the battery cooling expansion valve 19 is disposed in the vicinity of the battery cooling evaporator 18, the liquid refrigerant that has passed through the branch portion 20 is transferred from the branch portion 20 to the battery. After flowing through a long section to the cooling expansion valve 19, the pressure is reduced by the battery cooling expansion valve 19 and flows into the battery cooling evaporator 18. The density of the liquid refrigerant is 1150 kg / m ³ at 40 ° C. For this reason, when the section from the branch portion 20 to the battery cooling expansion valve 19 is constituted by a refrigerant pipe having an inner diameter of 6 mm and the length of the refrigerant pipe is assumed to be 5 m, the refrigerant pipe when the refrigerant temperature is 40 ° C. The amount of the refrigerant inside is 163 g.

On the other hand, in the present embodiment, since the battery cooling expansion valve 19 is disposed in the vicinity of the branch portion 20, the liquid refrigerant that has passed through the branch portion 20 is immediately decompressed by the battery cooling expansion valve 19 and is then discharged. It becomes a liquid two-phase refrigerant, flows through a long section from the battery cooling expansion valve 19 to the battery cooling evaporator 18 and flows into the battery cooling evaporator 18. The density of the gas-liquid two-phase refrigerant is 100 kg / m ³ at 10 ° C. For this reason, when the section from the battery cooling expansion valve 19 to the battery cooling evaporator 18 is constituted by a refrigerant pipe having an inner diameter of 10.3 mm and the length of the refrigerant pipe is assumed to be 5 m, the refrigerant temperature is 10 ° C. The amount of refrigerant in the refrigerant pipe at this time is 42 g.

  Thus, according to the present embodiment, the amount of refrigerant in the second forward path 23 can be significantly reduced. As a result, it is possible to reduce the amount of refrigerant enclosed in the entire refrigeration cycle and to reduce the difference in required refrigerant amount for each operation mode.

  Here, if the battery cooling expansion valve 19 is disposed on the side closer to the branch portion 20 than the battery cooling evaporator 18 in the second forward path 23, unlike the present embodiment, the expansion of the battery cooling in the second forward path 23 is performed. Even when the section from the valve 19 to the battery cooling evaporator 18 is configured by a single pipe, the amount of refrigerant existing in the second forward path 23 can be reduced as in the present embodiment.

  However, in this case, as a contradiction, a new problem arises in that the gas-liquid two-phase refrigerant receives heat from the outside when flowing through the single pipe, and the cooling performance of the battery cooling evaporator 18 is lowered.

  That is, since the refrigerant pipes constituting the second forward path 23 and the second return path 26 are arranged on the lower side of the vehicle, the temperature around the refrigerant pipe is often high due to the influence of reflection from the road surface. .

  In the case where the battery cooling expansion valve 19 is arranged closer to the battery cooling evaporator 18 than the branch portion 20 as in the prior art, as shown in FIG. A liquid refrigerant at a high temperature, for example, 40 ° C. flows through the refrigerant pipe 101 in a long section up to 19, and a gas refrigerant at a low temperature, for example, 15 ° C. flows through the refrigerant pipe 102 from the battery cooling evaporator 18 to the junction 24. For this reason, even if the external temperature is high, for example, 35 ° C., the temperature difference between the liquid refrigerant and the outside is small, and the amount of heat received is proportional to the temperature difference, so the amount of heat received from the outside of the liquid refrigerant is small.

  However, the battery cooling expansion valve 19 is disposed in the second forward path 23 on the side closer to the branch portion 20 than the battery cooling evaporator 18, and as shown in FIG. When the section from the evaporator 18 to the evaporator 18 is constituted by the single pipe 103 and the section from the battery cooling evaporator 18 to the junction 24 is constituted by the single pipe 104, the single pipe 103 is cooled at a low temperature, for example, 10 ° C. The phase refrigerant flows, and a gas refrigerant at a low temperature, for example, 15 ° C. flows through the other single pipe 104. For this reason, when the external temperature is high, for example, 35 ° C., the temperature difference between the gas-liquid two-phase refrigerant flowing through the single tube 103 and the outside is large, so the amount of heat received from the outside of the gas-liquid two-phase refrigerant increases.

  For this reason, the refrigerant state at the refrigerant inlet 18a of the battery cooling evaporator 18 is in the position indicated by a broken line in the Mollier diagrams of FIGS. 6 and 7, and the refrigerant inlet 18a and the refrigerant outlet of the battery cooling evaporator 18 are located. The enthalpy difference of 18b is small, and the cooling performance of the battery cooling evaporator 18 is lowered.

  Therefore, in the present embodiment, as shown in FIG. 4, the section 23b in which the gas-liquid two-phase refrigerant flows in the second forward path 23 is configured by the inner pipe 28a of the double pipe 28, and a part 26a of the second return path 26 is formed. The outer tube 28b of the double tube 28 is used. Thereby, according to this embodiment, since the low-temperature gas refrigerant which flows through the outer pipe 28b has a role of a heat insulating material, compared with the case where the second forward path 23 is constituted by the single pipe 103, the second forward path 23 is Heat receiving from the outside of the flowing gas-liquid two-phase refrigerant can be suppressed.

  For this reason, the refrigerant state at the refrigerant inlet 18a of the battery cooling evaporator 18 is the position of the black circle in the Mollier diagrams of FIGS. 6 and 7, and the second forward path 23 is constituted by the single tube 103. In comparison, the enthalpy difference between the refrigerant inlet 18a and the refrigerant outlet 18b of the battery cooling evaporator 18 increases.

  Therefore, according to the present embodiment, the cooling performance of the battery cooling evaporator 18 can be improved as compared with the case where the second forward path 23 is configured by the single tube 103.

  In the present embodiment, the heat insulating material is not wound around the double pipe 28, but the heat insulating material may be wound around the double pipe 28. Thereby, the heat receiving from the outside of a gas-liquid two-phase refrigerant | coolant can be suppressed more. In the case where a heat insulating material is wound around the double pipe 28, the space between the inner pipe 28a and the outside air is reduced by both the low-temperature gas refrigerant flowing through the outer pipe 28b and the heat insulating material around the double pipe 28. Insulated. For this reason, compared with the case where the second forward path 23 is constituted by a single pipe 103 and the heat insulating material is wound around the single pipe 103, the heat insulating material necessary for obtaining the same heat insulating performance is reduced, and The thickness of the insulation material to be rolled can be reduced.

(Second Embodiment)
In the first embodiment, a receiver cycle intended for cooling is used as the basic cycle of the refrigeration cycle apparatus 10, but in this embodiment, as shown in FIG. 10, a heat pump cycle capable of performing both cooling and heating. Is used. Other configurations are the same as those of the first embodiment.

  This heat pump cycle is an accumulator cycle using an accumulator 61 instead of the gas-liquid separator 14 of the first embodiment. This heat pump cycle includes a check valve provided in the indoor condenser 62, the heating expansion valve 63, and the refrigerant flow path 21 in addition to the compressor 11, the outdoor condenser 12, the cooling expansion valve 16, and the indoor evaporator 17. 64 and a bypass opening / closing valve 65 a provided in the bypass flow path 65.

  The accumulator 61 is a gas-liquid separator that separates the gas-liquid refrigerant sucked into the compressor 11 and stores excess refrigerant in the cycle.

  The indoor condenser 62 is disposed in the casing 31 of the indoor air conditioning unit 30. The indoor condenser 62 is used for heating to heat the indoor blown air while radiating the refrigerant by heat exchange between the high-pressure refrigerant discharged from the compressor 11 and the indoor blown air when heating the vehicle interior. It is a heat exchanger.

  The heating expansion valve 63 is a decompressor that decompresses the refrigerant that has flowed out of the indoor condenser 62 when heating the passenger compartment. The heating expansion valve 63 includes a valve body configured to be able to change the throttle opening (valve opening) from fully closed to fully open, and an electric actuator that changes the throttle opening (valve opening) of the valve body. The operation of the electric expansion valve is controlled by a control signal output from the control device.

  The bypass flow path 65 is a refrigerant flow path that guides the refrigerant flowing out of the outdoor condenser 12 to the accumulator 61 by bypassing the indoor evaporator 17 and the battery cooling evaporator 18. The bypass opening / closing valve 65a is an electromagnetic valve whose opening / closing operation is controlled by a control voltage output from the control device. The presence / absence of the refrigerant flow in the bypass passage 65 is switched by opening and closing the bypass opening / closing valve 65a.

  Also in this embodiment, there exists an effect similar to 1st Embodiment.

  In this embodiment, an electric expansion valve is used as the heating expansion valve 63, but a fixed throttle such as a capillary may be used instead of the electric expansion valve. In this case, a bypass path that bypasses the heating expansion valve 63 and flows the refrigerant, and an on-off valve that opens and closes the bypass path are provided. In the cooling operation mode, the refrigerant is caused to flow by bypassing the heating expansion valve 63 by opening the on-off valve.

(Third embodiment)
In the second embodiment, a heat pump cycle that can perform both cooling and heating is used as the basic cycle of the refrigeration cycle apparatus 10, but in this embodiment, as shown in FIG. 11, an accumulator cycle that performs only cooling is used. Used.

  In this accumulator cycle, the indoor condenser 62, the heating expansion valve 63, the check valve 64, the bypass passage 65, and the bypass opening / closing valve 65a are omitted from the accumulator cycle shown in FIG. Also in this embodiment, there exists an effect similar to 1st Embodiment.

(Fourth embodiment)
The present embodiment is different from the first embodiment in the structure of the double pipe 28, and the other configurations are the same as those in the first embodiment. This embodiment can also be applied to the second and third embodiments.

  As shown in FIG. 12, in this embodiment, a double tube 28 having a spiral structure is used. The double pipe 28 is the same as the double pipe 28 of the first embodiment in that the inner pipe 28c is located inside the outer pipe 28d, and the inner pipe 28c and the outer pipe 28d covering the inner pipe 28c are provided. It is.

  However, in the double tube 28 of the present embodiment, the inner diameter of the outer tube 28d and the outer diameter of the inner tube 28c are the same, and a spiral groove 28e forming a refrigerant flow path is formed on the outer surface of the inner tube 28c. This is different from the double tube 28 of the first embodiment.

  The groove 28e of the inner tube 28c and the inner surface of the outer tube 28d constitute a part 26a of the second return path 26. Therefore, the gas refrigerant flowing out of the battery cooling evaporator 18 flows along the groove 28e while swirling between the outer surface of the inner tube 28c and the inner surface of the outer tube 28d.

(Fifth embodiment)
In the first to fourth embodiments, the battery cooling evaporator 18 is a heat exchanger for exchanging heat between the blown air for the battery and the refrigerant, but in this embodiment, as shown in FIG. As an evaporator, a water-refrigerant heat exchanger 71 that exchanges heat between cooling water for cooling the battery and the refrigerant is used. Note that the present embodiment is applicable to any of the first to fourth embodiments.

  The water-refrigerant heat exchanger 71 constitutes the cooling water circuit 50a together with the water pump 52a and the battery pack 501.

  The cooling water circuit 50a is a circuit that circulates cooling water for cooling the secondary battery 53, for example, an ethylene glycol aqueous solution. In the cooling water circuit 50a, a water pump 52a, a cooling water passage formed inside or outside the secondary battery 53 in the battery pack 501, and a water-refrigerant heat exchanger 71 are sequentially connected in an annular manner by a pipe 51a. It is configured by

  The water pump 52a pumps the cooling water, and is an electric water pump whose operation (cooling water pumping ability) is controlled by a control signal output from the control device. The operation of the water pump 52a is controlled in the same manner as the blower 52 in each operation mode described in the first embodiment.

  The water-refrigerant heat exchanger 71 is a heat exchanger that includes a refrigerant passage 72 through which refrigerant flows and a water passage 73 through which cooling water flows, and exchanges heat between the cooling water and the refrigerant. In other words, the water-refrigerant heat exchanger 71 is a heat exchanger that indirectly exchanges heat between the refrigerant and the secondary battery 53 via the cooling water.

  Further, on the input side of the control device of the present embodiment, an inlet side water temperature sensor 54 that detects the temperature of the cooling water flowing into the cooling water passage of the secondary battery 53, and the cooling that flows out of the cooling water passage of the secondary battery 53. An outlet side water temperature sensor 55 that detects the temperature of the water is connected. For example, in the battery cooling single operation mode, the control device controls the refrigerant discharge capacity of the compressor 11 based on the detected temperatures of the battery temperature sensor 42 and the inlet side and outlet side water temperature sensors 54 and 55.

  Therefore, when the refrigeration cycle apparatus 10 according to the present embodiment is operated, in the battery cooling + cooling operation mode and the battery cooling single operation mode, the refrigerant decompressed by the battery cooling expansion valve 19 is transferred to the water-refrigerant heat exchanger 71. Cooling water flowing through the water passage 73 by flowing into the refrigerant passage 72 can be cooled. Thereby, the secondary battery 53 can be cooled.

  Even if the water-refrigerant heat exchanger 71 is used as in the present embodiment, the same effects as in the first embodiment can be obtained. In this embodiment, the cooling water is used as the cooling liquid for cooling the secondary battery 53, but other cooling liquid such as oil may be used.

(Sixth embodiment)
In this embodiment, as shown in FIG. 14, a heat exchanger 81 that directly exchanges heat between the secondary battery 53 and the refrigerant is used as a battery cooling evaporator. Note that the present embodiment is applicable to any of the first to fifth embodiments.

  The heat exchanger 81 is disposed in the battery pack 502 together with the secondary battery 53. The heat exchanger 81 is a heat exchanger that directly exchanges heat between the refrigerant and the secondary battery 53. The heat exchanger 81 is constituted by a refrigerant passage provided inside or outside the secondary battery 53, for example.

  Therefore, when the refrigeration cycle apparatus 10 of the present embodiment is operated, the refrigerant depressurized by the battery cooling expansion valve 19 is transferred to the heat exchanger in the battery pack 502 in the battery cooling + cooling operation mode and the battery cooling single operation mode. By flowing into 81, the secondary battery 53 can be cooled.

  Even if the secondary battery 53 is directly cooled by the refrigerant as in the present embodiment, the same effects as those of the first embodiment can be obtained.

(Other embodiments)
(1) In each embodiment described above, the branching portion 20 is provided at a position away from the outdoor condenser 12, but the branching portion 20 may be provided at the refrigerant outlet of the outdoor condenser 12. Therefore, “the refrigerant flow downstream side of the radiator” described in the claims includes not only the position away from the refrigerant outlet of the radiator but also the refrigerant outlet of the radiator.

  Similarly, in each of the embodiments described above, the merging portion 24 is provided at a position away from the compressor 11, but the merging portion 24 may be provided at the refrigerant inlet of the compressor 11. Therefore, “the refrigerant flow upstream side of the compressor” recited in the claims includes not only the position away from the refrigerant inlet of the compressor but also the refrigerant inlet of the compressor.

  (2) In each of the above-described embodiments, the part 26 a of the second return path 26 is constituted by the outer pipe 28 b of the double pipe 28, but the entire second return path 26 is constituted by the outer pipe 28 b of the double pipe 28. It may be configured.

  (3) In each of the above-described embodiments, the double pipe 28 has a smaller flow passage cross-sectional area S2 of the outer pipes 28b and 28d than the flow passage cross-sectional area S1 of the inner pipes 28a and 28c. Both of the channel cross-sectional areas S1, S2 may be the same. In this case, a pressure reducer such as a fixed throttle is added to the second return path 26 to increase the pressure loss of the refrigerant flowing through the second return path 26. Thereby, similarly to 1st Embodiment, the blowing air temperature of the evaporator 18 for battery cooling can be made higher than the blowing air temperature of the indoor evaporator 17. FIG.

  (4) In each of the above-described embodiments, the mechanical expansion valve is used as the cooling expansion valve 16 and the battery cooling expansion valve 19, but an electric expansion valve may be used. In the case of using an electric expansion valve, the first and second on-off valves 22a and 23a can be omitted by using a valve element whose valve opening can be fully closed.

  (5) In each of the above-described embodiments, the case where the operation mode is selected by the selection switch has been described. However, the control device 40 may automatically select the operation mode.

  (6) In each of the above-described embodiments, the example in which the first cooling object is indoor blowing air that is blown into the vehicle interior and the second cooling object is the secondary battery 53 has been described. The second cooling object is not limited to these.

  The first cooling object may be indoor blown air, and the second cooling object may be a device mounted on a vehicle other than the secondary battery 53. Examples of such devices include an internal combustion engine (engine), an electric motor, an inverter, and the like.

  Both the first and second cooling objects may be indoor blown air. In this case, for example, the indoor air blown to the front seat in the vehicle interior is cooled by the indoor evaporator 17 described in the first embodiment, and the battery cooling evaporator 18 is used as the rear seat evaporator. The blower air for room blown out to the rear seat of the vehicle interior may be cooled by the battery cooling evaporator 18. According to this, it is possible to cool the rear seat as a dual air conditioner. Not only the indoor blown air blown to the rear seat, but also the indoor blown air blown to a seat other than the front seat such as the second row of the third row seats may be cooled. Further, the first and second objects to be cooled may be indoor blown air blown to the right and left sides of the front seat in the vehicle interior.

  Further, the first and second cooling objects may be devices mounted on the vehicle. Examples of such devices include a secondary battery 53, an internal combustion engine (engine), an electric motor, an inverter, and the like.

  (7) In each of the above-described embodiments, an HFC refrigerant or the like is used as the refrigerant and the refrigeration cycle apparatus 10 constitutes a subcritical refrigeration cycle. A supercritical refrigeration cycle in which the internal pressure exceeds the critical pressure of the refrigerant may be configured.

  (8) In the first and second embodiments, the refrigeration cycle apparatus 10 according to the present invention is applied to a hybrid vehicle that obtains driving force for vehicle travel from both an internal combustion engine and an electric motor. You may apply to the electric vehicle which obtains force from the electric motor for driving | running | working.

  Moreover, in each above-mentioned embodiment, although the refrigeration cycle apparatus 10 which concerns on this invention was applied to the vehicle, you may apply other than a vehicle.

  (9) The present invention is not limited to the above-described embodiment, and can be appropriately changed within the scope described in the claims. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes.

10 Refrigeration cycle equipment 11 Compressor 12 Outdoor condenser (heat radiator)
16 Cooling expansion valve (first decompressor)
17 Indoor evaporator (first evaporator)
18 Battery cooling evaporator (second evaporator)
19 Battery cooling expansion valve (second decompressor)
20 Branching portion 22 First outgoing route 23 Second outgoing route 28 Double pipe

Claims (4)

A compressor (11) for compressing and discharging the refrigerant;
A radiator (12) for radiating the refrigerant discharged from the compressor;
First and second decompressors (16, 19) disposed in parallel on the refrigerant flow downstream side of the radiator and depressurizing the refrigerant flowing out of the radiator,
A first evaporator (17) for cooling the first cooling object and evaporating the refrigerant by heat exchange between the refrigerant decompressed by the first decompressor and the first cooling object;
A second evaporator (18, 71, 81) for cooling the second cooling object and evaporating the refrigerant by heat exchange between the refrigerant decompressed by the second decompressor and the second cooling object;
A refrigerant flow path branched from a branch part (20) provided on the downstream side of the refrigerant flow of the radiator, wherein the first and second refrigerant guides the refrigerant from the branch part to the refrigerant inlets of the first and second evaporators. 2 outbound routes (22, 23),
A refrigerant flow path that merges with a merging portion (24) provided on the upstream side of the refrigerant flow of the compressor, wherein the first and second refrigerant channels guide the refrigerant from the refrigerant outlet of the first and second evaporators to the merging portion. 2 return paths (25, 26),
The second forward path (23) has a longer refrigerant flow path length than the first forward path (22),
The second pressure reducer (19) is disposed closer to the branch portion than the second evaporator in the second forward path,
Of the second forward path, the portion (23b) on the downstream side of the refrigerant flow with respect to the second decompressor has a double pipe (28) having an inner pipe (28a, 28c) and an outer pipe (28b, 28d) covering it. ) Of the inner pipe,
At least a part of the second return path (26) is constituted by the outer pipe.   The refrigerant pressure at the refrigerant outlet of the second evaporator is higher than the refrigerant pressure at the refrigerant outlet of the first evaporator in the operation mode in which the refrigerant flows through both the first and second evaporators. The flow path cross-sectional area (S2) of the outer pipe is smaller than the flow path cross-sectional area (S1) of the inner pipe in at least a part of the double pipe. Refrigeration cycle equipment. The first cooling object is indoor air blown into the vehicle interior,
The refrigeration cycle apparatus according to claim 1 or 2, wherein the second cooling object is a device mounted on a vehicle. The refrigeration cycle apparatus according to claim 3, wherein the device mounted on the vehicle is a secondary battery.

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